Punch rivet and die

ABSTRACT

A punch rivet and a die for the production of a punch rivet connection are described. The punch rivet is characterized by special rivet foot and underhead geometries. In the region of the rivet foot, the shank outer face and shank inner face are connected by way of a small radially outer radius and a larger radially inner radius, which radii merge into one another tangentially. The angle that the common tangent encloses with a radial plane is in the range of 10°±20°. The die is preferably matched to the described punch rivet, but can also be used in combination with conventional punch rivets.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a divisional of U.S. application Ser. No.12/305,821, which is a US National Stage of PCT/EP2007/005376 filed onJun. 19, 2007 and which published as WO 2007/147551 on Dec. 27, 2007.This application also claims the right of priority granted under 35U.S.C. §§119 and 365 of German Application No. 10 2006 028 537.9 filedon Jun. 21, 2006. The disclosure of each of these applications isincorporated by reference herein in its entirety.

The present invention relates to a punch rivet that can be embodied as asimple rivet or else as a functional element such as, for example, apunch bolt or punch nut. In particular the invention relates to a punchrivet in the form of a semi-hollow punch rivet or hollow punch rivet forthe production of a punch rivet connection to one or more plate-shapedparts to be joined (plates). The invention furthermore relates to a diethat can be used in the production of the punch rivet connection. Thedie is preferably matched in a special manner to the geometry of thepunch rivet, but can also be used in combination with conventional punchrivets.

Punch riveting as a joining method has gained increasing importance inthe recent past. An important parameter for the joining process as wellas the connection quality of the punch rivet connection is the geometryof the punch rivet. Numerous different geometries of the punch rivet areknown in the prior art, see e.g. EP 0 720 695, EP 1 064 466, EP 1 229254, EP 1 387 093, DE 44 31 769, DE 203 19 610 U1, DE 200 01 103 U1, US2004/0068854 A1, JP 2001159409A, JP 09317730A, among others.

The punch rivet according to the above-mentioned EP 0 720 695, which isusually called a C-rivet, is used on a large scale in the automotiveindustry, but also in other technical areas. The C-rivet is asemi-hollow punch rivet with a rivet head and a rivet shank with acentral shank hole, of which the rivet head has a flat upper side and acylindrical head outer face and the rivet shank has a cylindrical shankouter face and a cylindrical shank inner face delimiting the centralshank hole. The cylindrical head outer face and the cylindrical shankouter face are connected together directly by a relatively large radius.In the foot region of the punch rivet the central shank hole is embodiedas a cone, wherein the cone flanks are to be slightly curved accordingto the details in this document. By these means in the scope of theproduction engineering possibilities, a quasi “sharp edge” is created atthe outer edge of the rivet shank, which sharp edge in practice isgenerally somewhat chamfered. According to the details in this document,the opening angle of the cone can be between 25° and 120°.

In the prior art the starting point for configuring punch rivets wasusually the so-called “pierce and roll” behavior of the punch rivets.“Pierce and roll” means that the punch rivet is spread (roll) into thelower sheet as soon as possible after the penetration (pierce), in orderto achieve the greatest possible spreading and thus the largest possibleundercut of the punch rivet in the punch rivet connection. Theseconsiderations have led to rivet geometries such as, for example, thatof the C-rivet and corresponding dies, for example with a mandrel.

Although the C-rivet has proved to be successful in practice, furtherimprovements are desirable such as, e.g., an improved bearing behaviorof the punch rivet connection and an improved cost-effectiveness of thejoining method.

The object of the present invention is to create a punch rivet for theproduction of a punch rivet connection with one or more parts to bejoined, which rivet allows an optimization of the bearing behavior ofthe punch rivet connection as well as a particularly economical joiningprocess, in particular by a lowering of the requirements for strengthand hardness of the punch rivet material and a reduction in the settingforces required for the joining process. Furthermore, a die suitable forthis is to be created that is preferably matched to the geometry of thepunch rivet embodied according to the invention, but that can also beused in combination with other rivet geometries.

Punch rivets according to the present invention for attaining thisobject are defined in claims 1 and 2.

The punch rivet embodied according to the invention is characterized inparticular by a special rivet foot geometry and a special underheadgeometry, as are given by claims 1 and 2.

According to the solution of claim 1, the shank outer face and shankinner face at the rivet head end are connected by means of a radiallyouter first radius R₁ and a radially inner second radius R₂ that mergeinto one another tangentially. The common tangent of R₁ and R₂ enclosesan angle α of 10°±20° with a radial plane of the punch rivet. The firstradius R₁, which merges tangentially into the shank outer face or isreplaced by a chamfer of corresponding length, is 0.3±0.2 mm and thesecond radius R₂, which merges tangentially into the shank inner face,is (0.7 to 1.2) (d_(N)−d_(i))/2, in particular (0.8 to 1.0)(d_(N)−d_(i))/2. The factor (0.7 to 1.2) or (0.8 to 1.0) is preferablyselected to be increasingly larger as R₁ becomes larger.

If the result of radii R₁ and R₂ selected within the given value rangesis that no second radius R₂ can be found that is tangent to both thefirst radius R₁ and the shank inner face, according to the alternativesolution of claim 2 a third radius R₃ is provided between the secondradius R₂ and the shank inner face, which radius merges tangentiallyboth into the second radius R₂ and into the shank inner face and is0.8±0.4 mm. The angle α between the common tangent of R₁, R₂ and aradial plane of the punch rivet is then to be selected in the range of5°±10°.

The geometry in the underhead region of the rivet head is characterizedin both solutions in that the head outer face and the shank outer faceare connected through a conical or slightly curved underhead chamfer andan underhead radius, of which the underhead radius merges tangentiallyinto both the underhead chamfer and the shank outer face. In the case ofa conical underhead chamfer, the underhead chamfer encloses an angle βof 25°±10°, in particular 25°±7°, with a radial plane of the punchrivet. In the case of a slightly curved underhead chamfer, the curvatureradius is R₇≧2.0 mm.

The punch rivet geometry according to the invention means a turning awayfrom the “pierce and roll” behavior of the punch rivet explained above.As will be explained in more detail based on the Figures, the startingpoint for the present invention is the realization that in addition tothe quality criteria of the undercut of the spread punch rivet sectionand the axial minimum thickness of the die-side part to be joined(sheet) at the rivet foot, other quality criteria of the punch rivetconnection must be brought in for the achievement of an optimum bearingbehavior. These criteria, as will be explained in more detail based onthe Figures, are the so-called engagement length L (engagement betweenthe outer face of the rivet foot and the die-side part to be joined),the so-called bearing depth T (axial component of the engagement lengthL), and the radial thickness t_(NF) of the die-side part to be joinedthat surrounds the rivet foot.

The rivet geometry was selected according to the invention such that theengagement length L, the bearing depth T, and the thickness t_(NF) ofthe punch rivet connection are maximized. The consideration in thisregard is that the bearing behavior of the punch rivet connection can beimproved if a maximizing of the undercut of the spread-out punch rivetsection is given up in favor of an improved “force closure” between therivet shank and the die-side part to be joined (sheet). An improved“force closure” results through an enlargement of the cross sections andouter faces of the punch rivet in engagement on the one hand and theparts to be joined on the other hand, through which the special loadingof the force-transmitting areas is minimized. Moreover this leads to areduction in the radial compression stresses, so that with externalloading of the punch rivet connection, the size of the total stressesresulting from the superimposition remains within bounds. Due to themaximizing of the engagement length L, the bearing depth T, and thethickness t_(NF) achieved through the invention, with adequate undercutof the spread-out punch rivet section and minimum axial thicknesst_(min) of the part to be joined, the surface pressing between punchrivet and parts to be joined is reduced, which again improves thestiffness and fatigue strength of the punch rivet connection. The rivetfoot geometry according to the present invention also leads to theresult that during the joining process the punch rivet penetrates thepunch-side part to be joined essentially in a cutting process and thatthe rivet shank is not spread until during penetration into the die-sidepart to be joined. The result is a less resistant sliding of the rivetfoot along the parts to be joined. These facts lead to a minimizing ofthe setting force required, the consequence of which in turn is that therequirements for hardness and strength of the punch rivet material areclearly reduced and the production and processing of the punch rivetsbecome simpler and much cheaper.

In a further development of the invention a specially dimensioned die isprovided for the punch rivet embodied according to the invention. A dieembodied according to the invention is defined in claim 19. Inaccordance with this, the following holds true for the die diameter

D _(M) =d _(N)+(0.6 to 1.5)2t _(M), in particular d _(N)+(0.7 to 1.2)2t_(M)

for parts to be joined that are made of a material with gooddeformability, in particular made of a wrought alloy, and

D _(M)≦2.2d _(N)

for parts to be joined that are made of a cast material or anothermaterial of low deformability, wherein d_(N) is the shank outer diameterof the rivet shank and t_(M) is the thickness of the die-side part to bejoined. The depth T_(M) for parts to be joined that are made of amaterial of good deformability is preferably in the range T_(M)=(1.0 to2.5) t_(M), in particular T_(M)=(1.1 to 2.2) t_(M). The depth T_(M) forparts to be joined that are made of materials of low deformability ispreferably ≦0.15 D_(M) and/or ≦t_(M).

The result of these formulas is that the die diameter is smaller than inthe prior art. The smaller die diameter in turn promotes the desiredreduction in the spreading-out of the rivet shank.

According to claim 20 a die embodied according to the invention ischaracterized in that the die has a central depression on the die floorthat during the joining process ensures pressure relief during thejoining process.

The punch rivet embodied according to the invention is particularlysuited for the joining of parts to be joined that are made ofhigher-strength steels, in particular AHSS steels as well as metastableaustenitic steels such as, e.g., H400. In principle, however, the punchrivet is suitable for the joining of parts to be joined that are made ofany materials including plastic. The punch rivet can be composed ofconventional materials, whereby however, as mentioned, hardness andstrength of the material can be much lower than in the prior art. Thereduction in the required setting forces made possible through theinvention and the substantial improvement in the bearing behavior makeit possible, for example, that with the claimed rivet geometry evenrivets of aluminum alloys such as, e.g., AlMgSi1 T6/T7 are suitable forthe riveting of aluminum semi-finished products.

The punch rivet embodied according to the invention can be a semi-hollowpunch rivet (in which the central shank hole is a blind hole) or ahollow punch rivet (in which the central shank hole is a through hole).The punch rivet can be a pure rivet or a functional element, inparticular a punch bolt or a punch nut.

The rivet shank can have a cylindrical shank outer face or an axiallyribbed shank outer face. The axial ribbing serves as an anti-rotationelement during the joining process, in particular when the punch rivetis embodied as a functional element. The axial ribbing of the shankouter face does not require any additional joining forces. This isadvantageous compared to star-shaped ribbings under the rivet head, asare known from the prior art.

If the punch rivet is embodied as a functional element, it can also beused in combination with a single part to be joined (sheet).

The rivet head is preferably embodied as a countersunk head. Dependingon the application case, however, a flat head can also be used.

Further advantageous embodiments and developments of the invention aredefined in the dependent patent claims.

Based on the drawings, further details of the invention and preferredembodiments of the invention are explained. They show:

FIG. 1 an axial section of a punch rivet embodied according to theinvention;

FIG. 2 a half axial section through a finished punch rivet connectionfor illustrating certain quality criteria of the punch rivet connection;

FIGS. 3 to 6 diagrammatic representations of a punch rivet process invarious operating phases;

FIG. 7 a sectional representation of a part of a modified die;

FIG. 8 an axial section through a modified embodiment of the punchrivet;

FIG. 9 a cross section in the view direction of the arrows IX-IX in FIG.8.

Based on FIG. 1 a specific exemplary embodiment of a semi-hollow punchrivet embodied according to the invention is described.

The punch rivet 2 is embodied rotation-symmetrically with respect to acentral axis X and is composed of a rivet head 4 and a rivet shank 6with a central shank hole 8 that is embodied as a blind hole. The rivethead 4 has a flat upper side 10 and a cylindrical head outer face 12.The head outer face 12 has a diameter d_(K) and an axial height H_(K).

The rivet shank 6 has a cylindrical shank outer face 14 and acylindrical shank inner face 16 that delimits the shank hole 8. Thecylindrical shank outer face 14 has a shank outer diameter d_(N), andthe cylindrical shank inner face has a shank inner diameter d_(i).

The head outer face 12 is connected to the shank outer face 14 via anunderhead chamfer 18 and a radius R₄ (the term “radius” in the presentscope is to be understood to mean an annular face that in an axialsection has the shape of an arc with the radius R).

The radius R₄ runs tangentially both into the underhead chamfer 18 andalso into the shank outer face 14, while the underhead chamfer 18directly adjoins the head outer face 12 (e.g., via a radius or a sharpedge). The underhead chamfer 18 encloses an angle β with a radial planeof the punch rivet 2.

At the rivet foot end the shank outer face 14 is connected to the shankinner face 16 via a first radius R₁ with the center M1 and a secondradius R₂ with the center M2 as well as optionally a third radius R₃.The radius R₁ merges tangentially both into the shank outer face 14 andinto the second radius R₂. The second radius R₂ merges tangentiallyeither directly into the shank inner face 16 or into the third radiusR₃, which in turn merges tangentially into the shank inner face 16.

As can be seen clearly in FIG. 1, the radius R₁ is much smaller than theradius R₂. The common tangent Tan of the radii R₁ and R₂, which tangentstands perpendicular to the connectors of centers M1 and M2, encloses anangle α with a radial plane E of the punch rivet 2.

At the rivet head end, the shank hole 8 has a conical floor face 24 of acone angle γ that is connected to the shank inner face 16 by means of anouter shank hole radius R₅ and ends in a radius R₆ in the region of thecentral axis X. The shank hole 8 has a shank hole depth t_(B), which ismeasured from the rivet foot end to the point at which the notionalextensions of the conical floor face 24 and of the shank inner face 16intersect. The thickness of the rivet head 12 on the central axis X isdesignated D_(K).

Before going into the specific value ranges of the quantitiesdetermining the geometry of the punch rivet according to the invention,the basic considerations that led to the present invention will beoutlined with reference to FIG. 2. As has already been explained at theoutset, in the prior art when judging a finished punch rivet connection,on the one hand the undercut H of the spread rivet shank section and onthe other hand the axial minimum thickness t_(min) of the die-side partto be joined (sheet) are brought in as a quality criterion. In principlethe aim was to make the undercut H and the minimum thickness t_(min) aslarge as possible.

In contrast, the present invention starts from the consideration that inaddition to the undercut H and the minimum thickness t_(min), essentialquality criteria of the punch rivet connection are the engagement lengthL, the bearing depth T, and the radial thickness t_(NF) of the part tobe joined (sheet) that surrounds the rivet foot. As is shown by FIG. 2,the engagement length L is the length of the engagement between theouter face of the rivet shank 6 and the die-side part to be joined 26,and the bearing depth T is the axial component of the engagement lengthL. The radial thickness t_(NF) of the die-side part to be joined 26 thatsurrounds the rivet foot is measured at the radially outermost point ofthe rivet foot.

According to the teaching of the present invention, in principle the aimis to maximize the engagement length L, the bearing depth T, and theradial thickness t_(NF). As was determined on the basis of extensivetests, in this manner the bearing behavior of the punch rivet connectioncan be improved and optimized, as will be explained in more detailbelow.

Other considerations on which the invention is based relate to theconfiguration of the rivet head, the rivet shank, and the die used toproduce the rivet connection, as will likewise be explained in moredetail below.

Configuration of the Rivet Foot

The geometry of the rivet foot according to the exemplary embodiment ofthe present invention shown is determined by the following value ranges:

R ₁=0.3±0.2 mm

R ₂=(0.7 to 1.2)(d _(N) −d _(i))/2, in particular R ₂=(0.8 to 1.0)(d_(N) −d _(i))/2

α=10°±20°.

The radius R₁ can be replaced by a chamfer of, for example, 45°, as longas the length of the chamfer is not greater than the correspondingsecant line of the radius R₁.

These value ranges hold true for the case in which the radius R₂ mergesdirectly tangentially into the shank inner face 16. If no radius R₂ thattouches both the radius R₁ and also the shank inner face 16 can be foundwithin the given value range, the radius R₂ is to be connected to theshank inner face via a further radius R₃. The following value ranges arethen to be selected for R₃ and the angle α:

α=5°±10°

R ₃=0.8±0.4 mm.

If the radius R₁ is less than equal to 0.2 mm, the angle α isexpediently α=5°±10°. With a larger radius R₁ (up to 0.4 mm), the angleα can be α=10°±20°.

An essential parameter of the geometry of the rivet foot is the angle αthat the common tangent Tan of the radii R₁ and R₂ encloses with theradial plane E of the punch rivet. As is shown and results from thegiven value ranges, the angle α is very small and can even be negative.This makes it clear that the rivet foot, in contrast to the prior art,is embodied blunt to a certain extent, i.e. has no sharp-edged cuttingedge in the narrower sense. These facts have a considerable influence onthe punch rivet process and the embodiment of the punch rivetconnection, as will now be explained with reference to FIG. 3 throughFIG. 6, using as an example a punch rivet connection between two partsto be joined (sheets):

As is known, in punch riveting the parts to be joined 26, 28 are heldbetween the upper side of a die 30 and the lower side of a hold-downdevice 32. The die 30 has a cavity 34 that is delimited by a floor face36, preferably in the form of a projection (mandrel) and a cylindricalcircumferential face 38. During the joining process the punch rivet 2 ispressed into the parts to be joined 26, 28 by a punch (not shown) andshaped sections of the parts to be joined 26, 28 are hereby deformedinto the cavity 34 of the die 30. The punch rivet punches through thepunch-side part to be joined 28, hereby separates off a slug 28 a fromthe part to be joined 28, and deforms the die-side part to be joinedwithout punching through it. By these means a type of “driven head” isformed, so that the two parts to be joined 26, 28 are held togetherpositively between the rivet head 4 and the “driven head”.

The above-defined geometry of the rivet foot has the following effectson the joining process and the embodiment of the punch rivet connection:

a) In the first part of the joining process the rivet foot punchesthrough the punch-side part to be joined 28 without excessivedeformation of the part to be joined 28. This is therefore largely apure punching or cutting process.

b) Since in this punching process the rivet foot essentially penetratesthe punch-side part to be joined 28 in a cutting process, the rivet footand the rivet shank do not suffer any greater deformation. This isillustrated by FIG. 4 and FIG. 5. The consequence is that the settingforce required to punch through the punch-side part to be joined 28 isrelatively low.

c) The rivet foot now presses the punched-through slug 28 a downwardstogether with the die-side part to be joined 26 into the cavity 34 ofthe die 30, until the lower part to be joined 26 bears against a floorface 36 of the die 30.

d) When the die foot has punched through the punch-side part to bejoined 28, the rivet foot “slides” radially outwards and axiallydownwards on the face of the slug 28 a, so that the material of the slug28 a is extruded radially inwards inside the shank hole 8 and thedie-side part to be joined 26 is deformed radially outwards and axiallytowards the die floor (FIGS. 5, 6). The undercut H (FIG. 2) is formedhereby. The die-side part to be joined 26 surrounds the rivet foot,without the die-side part to be joined being thinned too greatlyradially and axially or even cut through.

In brief, the joining process is thus characterized in that thepunch-side part to be joined 28 is largely punched through in a purecutting process, without the rivet shank 6 and the punch-side part to bejoined 28 being deformed excessively, and that the expanding (spreading)of the rivet shank 6 does not take place until the penetration into thedie-side part to be joined 26. The result of this is that the engagementlength L, the bearing depth T, and the radial thickness t_(NF) of thedie-side part to be joined 26 surrounding the rivet foot are maximized.

The consequence is that the force closure (friction closure) between therivet shank 6 and the parts to be joined 26, 28 supplies an essentialcontribution to the bearing behavior. In particular the specific loadingof the force-transmitting regions between the punch rivet 2 and theparts to be joined 26, 28 is minimized hereby. Moreover a reduction inthe radial compression stresses within the punch rivet connectionresults, so that with an outer loading of the punch rivet connection,the sum of outer and inner stresses remains within justifiable limits.Furthermore, through the maximization of L, T, and t_(NF) with anadequate undercut H and minimum thickness t_(min), the surfacecompression between the punch rivet 2 and the parts to be joined 26, 28is reduced, by means of which the stiffness and fatigue strength of thepunch rivet connection are improved.

A further important advantage of this configuration of the punch rivetconnection comprises, as already mentioned, a significant reduction inthe setting force required to produce the punch rivet connection. Thisnot only has an advantageous effect on the configuration and theoperation of the setting tool, but above all results in the requirementsfor hardness and strength of the punch rivets being clearly reduced.Thus punch rivets for the production of a punch rivet connection betweenparts to be joined made of specified materials can be used whosehardness and strength are considerably lower than in the prior art. Forexample, rivets of conventional aluminum alloys such as e.g. AlMgSi1 canbe used for the riveting of aluminum semi-finished products.

A further advantage of the described embodiment of the punch rivetconnection is that gaps between the punch rivet on the one hand and theparts to be joined on the other hand, as well as between the parts to bejoined together, are avoided or at least minimized. Together with theother properties of the punch rivet connection, this has an advantageouseffect on the bearing behavior and in particular on the fatigue strengthbehavior of the punch rivet connection.

Configuration of the Rivet Head

The configuration of the rivet foot must be seen in combination with theconfiguration of the rest of the punch rivet, in particular the rivethead, the rivet shank, and the shank hole.

In the exemplary embodiment shown, the rivet head 4 is embodied as acountersunk head with a conical underhead chamfer 18 that is connectedto the shank outer face 14 through the radius R₄ and intersects thecylindrical head outer face 12.

The following holds true for the head diameter d_(K) of the rivet head 4embodied as a countersunk head:

d _(K)=(1.3 to 1.8)d _(N), in particular d _(K)=(1.4 to 1.65)d _(N).

The following holds true for the axial length H_(K) of the head outerface 12:

H _(K)=(0.025 to 0.2)d _(N), in particular H _(K)=(0.025 to 0.12)d _(N).

H_(K) must be selected larger as the head diameter d_(N) increases. Thegiven ranges hold true in particular for shank outer diameter d_(N)≦6mm.

The angle β, which the underhead chamfer 18 encloses with a radialplane, is in the range of 25°±10°, in particular 25°±7°. The radius R₄is 0.6±0.4 mm, in particular 0.5±0.2 mm.

As indicated by a dashed line on the right-hand side of FIG. 1, theunderhead chamfer can also be embodied slightly curved, wherein thecurvature should deviate only slightly from the conical face and thecurvature radius should be R₇≧2.0 mm.

The angle β or the radius R₇ and the radius R₄ are hereby selected suchthat the force for closing the gap between the rivet head 4 and thepunch-side part to be joined 28 (FIG. 2 and FIG. 6) and thus the settingforce is as low as possible. The size of the setting force is influencedto a considerable extent by the difference between the angle β or theradius R₇ of the underhead chamfer 18 and the corresponding angle of theupper side of the punched-through punch-side part to be joined 28 aswell as by the size of the radius R₄.

If the angle β is too large or the radius R₇ is too small, a very highsetting force is required in order to close the gap between headunderside and punch-side part to be joined 28. If the angle β is toosmall, a gap forms between the punch rivet 2 and the punch-side part tobe joined 28 in the region of the radius R₄. The rivet head 4 is thenloaded to bending and can easily break off when an attempt is made toclose this gap by means of a correspondingly large setting force.

If the radius R₄ is selected too large (as is the case in the prior artfor example with the so-called C-rivet), the punch rivet mustcorrespondingly deform the adjacent corner of the punched-throughpunch-side part to be joined 28 in the region of the radius R₄ andhereby must partially also displace material of the punch-side part tobe joined 28 radially outwards. A very high force is required for this,which in turn increases the size of the required setting force. If theradius R₄ is too small, the notch effect caused hereby can lead to abreakage of the rivet head 4.

The described rivet head embodied as a countersunk head, in particularthe above-defined underhead geometry, is quite generally suited to theriveting of parts to be joined that are made of all metallic materialsand if desired also of other materials. In the joining of plastics, inparticular fiber-reinforced plastics, rivet heads with a flat seating,so-called flat heads, with small transition radii to the rivet head canalso be expedient. In these cases in general the head diameter d_(K) isselected larger than with the countersunk head rivets, in order toreduce the specific surface loading between the rivet head underside andthe upper side of the punch-side part to be joined. The size of therivet head diameter then lies outside the above-defined range.

Configuration of the Rivet Shank with Shank Hole

In the prior art the shank outer diameter d_(N) of semi-hollow punchrivets is usually between 3 and 8 mm, and the wall thickness of therivet shank is usually between 0.5 and 2.0 mm. The total length of thepunch rivet is seldom greater than 10 mm. Semi-hollow punch rivets usedin automotive engineering to connect car body components frequently havea shank outer diameter d_(N) of 5.3 mm or 3.2 mm.

The shank outer diameter d_(N) can also be selected in these ranges forpunch rivets according to the present invention. Preferably the shankouter diameter d_(N) is in the range of 5.0 to 6.0 mm. As will beexplained in more detail, however, with punch rivets according to thepresent invention the shank outer diameter d_(N) can be selected inprinciple somewhat larger than in the prior art, since the punch rivetsembodied according to the invention require lower setting forces.

The shank inner diameter d_(i) is preferably (0.5 to 0.8) d_(N). Thefollowing value ranges hold true preferably for the quantities R₅, R₆,γ, T_(B) and D_(K):

R ₅=0.7±0.5 mm, in particular R ₅=0.8±0.3 mm

R ₆=0.9±0.5 mm, in particular R ₆=0.8±0.3 mm

γ=110° to 140°, in particular γ=110° to 130°

t _(B)≧0.2d _(N), in particular t _(B)≧0.3d _(N)

D _(K)≧0.15d _(N).

The given value ranges for the quantities determining the shank geometryensure that the rivet shank 6 can be endowed in every application casewith an adequate pressure stability (no inadmissible compressing duringthe joining process), an adequate buckling strength and bulging strength(no buckling and/or bulging of the rivet shank during the joiningprocess) and an adequate bending strength and compression strength(targeted deformation during the joining process).

The geometry shown and in particular the angle γ of the shank hole wereselected in order to facilitate the manufacture of the shank hole. Itshould be pointed out, however, that the geometry of the shank hole canalso be selected to be different. Thus for example the floor of theshank hole can be embodied in the shape of a dome, that is, in the formof an arc with a transition to the shank inner face 16 via the radii R₅.Other hole geometries are also possible.

Production of the Punch Rivet

As already mentioned, the punch rivets according to the presentinvention enable distinctly reduced setting forces in comparison withthe prior art. Tests have shown that the setting forces required for theproduction of the punch rivet connection are lower by an order ofmagnitude of 20%. This in turn allows the shank outer diameter d_(N) andthus also the shank inner diameter d_(i) to be made larger than in theprior art, without endangering the pressure stability, buckling strengthand bulging strength, and the bending strength and compression strengthof the punch rivet.

An enlargement of the shank outer diameter d_(N) of the punch rivetenables a technically easier and more economical production of the punchrivet:

In the production of punch rivets by cold forming, the shank hole isshaped by means of a so-called pin. The smaller the cross section of theshank hole 16 and thus of the pin, the more difficult the production ofthe punch rivet.

It must be taken into consideration hereby that the costs for the rivetproduction depend essentially on the costs for the production tools,wherein the service life of the production tools plays a decisive role.An enlargement of the cross section of the shank hole and thus of thepin leads to a significant facilitation of the production andmoreover—because of the improved guiding of the pin—to an improvement inthe production accuracy of the shank hole. The service life of theproduction tools is lengthened disproportionately by this, so that thecosts for the rivet production are correspondingly reduced.

With these considerations it must also be taken into account that asmall change in the shank outer diameter d_(N) can result in quite alarge change of the shank inner diameter d_(i), without impairing thestability of the punch rivet. A change in the shank outer diameter d_(N)by 0.3 mm for example allows a change in the shank inner diameter d, by0.4 mm, without the pressure stability of the rivet shank beingimpaired. A change in a shank inner diameter d_(i)=2.9 by 0.3 mm leadsto a cross section enlargement of the pin by 33%, and a change by 0.4 mmleads to a cross section enlargement of the pin by 41%.

It is clear from these numerical examples that the punch rivets embodiedaccording to the invention can be produced considerably moreeconomically than punch rivets of the prior art.

Configuration of the Die

The die 30 used in the production has a considerable influence on thejoining process and the formation of the punch rivet connection, inparticular the volume or the diameter D_(M) of the cylindricalcircumferential face 38 of the cavity 34 of the die 30, see FIGS. 2through 6.

The following preferably holds true for the diameter D_(M):

D _(M) =d _(N)+(0.6 to 1.5)2t _(M), in particular D _(M) =d _(N)+(0.7 to1.2)2t _(M)

for parts to be joined that are made of materials of good deformability,in particular wrought alloys. t_(M) is hereby the thickness of thedie-side part to be joined 26. Thus the diameter D_(M) of the die 30increases with the thickness of the die-side part to be joined 26.Expediently the depth T_(M) of the cavity 34 of the die 30 with thethickness of the die-side part to be joined 26 should also be selectedlarger. The following preferably holds true:

T _(M)=(1.0 to 2.5)t _(M), in particular T _(M)=(1.1 to 2.2)t _(M).

The value ranges given result in diameters D_(M) of the circumferentialface 38 of the dies that are small in comparison with the prior art.This reduction in the cavity of the die, in particular of the diameterD_(M), reduces the so-called “cut gap”, i.e. the gap between the shankouter diameter d_(N) and the die inner diameter, i.e. the diameterD_(M). This in turn promotes the processes explained in the context ofthe configuration of the rivet foot in the joining process. Inparticular the punch-through of the punch-side part to be joined 28 in a“cut process”, the deformation of the die-side part to be joined 26, andthe corresponding movements and deformations of the rivet shank 6 arepromoted by this.

The following preferably holds true for parts to be joined that are madeof cast materials as well as of other materials of low deformability orlow elongation at break such as e.g. magnesium:

D _(M)≦2.2d _(N)

T _(M)≦0.15D _(M).

In the exemplary embodiment of FIG. 3 through FIG. 6 the floor face 36of the die 30 is provided in the conventional manner with a mandrelprojecting upwards. FIG. 7 shows an embodiment according to theinvention of a die 30′, in which the floor face 36′ is provided with acentral depression 40. In the exemplary embodiment shown, the depression40 is embodied cylindrical and has a diameter D_(EB)≦0.5 D_(M) and adepth T_(EB)≧0.3 d_(N). The following holds true for the radius R_(EB):

R _(EB)≧0.3 mm, in particular 0.4 to 1.0 mm.

The depression 40 ensures a pressure relief during the joining process,through which excessive radial stresses in the punch rivet connectionare avoided and the danger of a crack formation is reduced. Expedientlyits dimensions—diameter and depth—can also be oriented to the diameterof the shank hole or the thickness of the die-side part to be joined andare then

D _(EB) ≧d _(i)

T _(EB)≧0.1T _(M) , e.g. ≧0.1 mm.

FIGS. 8 and 9 show a modified embodiment of a punch rivet 2′. Whereas inthe exemplary embodiment of FIG. 1 through FIG. 6 the shank outer face14 is embodied cylindrically, the shank outer face of the modified punchrivet 2′ is provided with an axial ribbing 42. The axial ribbing 42forms an anti-rotation element during the joining process, which isadvantageous in particular when the punch rivet is embodied as afunctional element (not shown) with a bolt-shaped or nut-shapedattachment on the rivet head. The ribbing 42 running axially moreoverensures a good guiding of the punch rivet 2′, without the requiredjoining force being increased by this.

What is claimed:
 1. A punch rivet with a rivet head and a rivet shankwith a central shank hole that have a common central axis X, wherein therivet head has an essentially cylindrical head outer face of a specifiedhead diameter d_(K), the rivet shank has a shank outer face of aspecified shank outer diameter d_(N) and a shank inner face of aspecified shank inner diameter d_(i) delimiting the central shank hole,the head outer face and the shank outer face are connected by means of aconical or slightly curved underhead chamfer and an underhead radius R₄,which radius merges tangentially both into the underhead chamfer andinto the shank outer face, and the shank outer face and the shank innerface are connected at the rivet foot end via a radially outer firstradius R₁ and a radially inner second radius R₂ that merge into oneanother tangentially, wherein the common tangent Tan encloses an angle αwith a radial plane of the punch rivet, wherein the first radius R₁merges tangentially into the shank outer face or is replaced by achamfer of corresponding length, and the second radius R₂ mergestangentially into the shank inner face, and wherein the following valueranges hold true for the first radius R₁, the second radius R₂, and theangle α:R ₁=0.3±0.2 mmR ₂=(0.7 to 1.2)(d _(N) −d _(i))/2α=10°±20°.
 2. The punch rivet according to claim 1, wherein thefollowing holds true for the second radius R₂:R ₂=(0.8 to 1.0)(d _(N) −d _(i))/2.
 3. The punch rivet according toclaim 1, wherein the conical underhead chamfer encloses an angleβ=25°±10°, in particular 25°±7°, with a radial plane of the punch rivet.4. The punch rivet according to claim 1, wherein the slightly curvedunderhead chamfer has a radius R₇≧2.0 mm.
 5. The punch rivet accordingto claim 1, wherein the following holds true for the underhead radiusR₄:R ₄=0.6±0.4 mm, in particular R ₄=0.5±0.2 mm.
 6. The punch rivetaccording to claim 1, wherein the following holds true for the shankinner diameter d_(i):d _(i)=(0.5 to 0.8)d _(N).
 7. The punch rivet according to claim 1,wherein the following holds true for the head diameter d_(K) of therivet head:d _(K)=(1.3 to 1.8)d _(N), in particular d _(K)=(1.4 to 1.65)d _(N). 8.The punch rivet according to claim 1, in which the rivet head end of theshank hole is embodied closed, characterized in that the closed end ofthe shank hole has a conical floor face that merges into the shank innerface via an outer shank hole radius R₅ and ends in an inner shank holeradius R₆ in the region of the central axis X.
 9. The punch rivetaccording to claim 1, wherein the following holds true for the axiallength H_(K) of the head outer face:H _(K)=(0.025 to 0.2)d _(N), in particular H _(K)=(0.025 to 0.12)d _(N).10. The punch rivet according to claim 9, characterized in that thefollowing holds true for the outer shank hole radius R₅:R ₅=0.7±0.5 mm, in particular R ₅=0.8±0.3 mm.
 11. The punch rivetaccording to claim 10, wherein the cone angle γ of the conical floorface is 110° to 140°, in particular 110° to 130°.
 12. The punch rivetaccording to claim 10, wherein the following holds true for the innershank hole radius R₆:R ₆=0.9±0.5 mm, in particular R ₆=0.8±0.3 mm.
 13. The punch rivetaccording to claim 10, wherein the following holds true for the deptht_(B) of the shank hole from the rivet foot end to the point at whichnotional extensions of the conical floor face and the shank inner faceintersect:t _(B)≧0.2d _(N), in particular t _(B)≧0.3d _(N).
 14. The punch rivetaccording to claim 10, wherein the following holds true for thethickness D_(K) of the rivet head on the central axis X:D _(K)≧0.15d _(N).
 15. The punch rivet according to one claim 1, whereinthe shank hole is embodied open at the rivet head end.
 16. The punchrivet according to claim 1, wherein it is embodied as a functionalelement, in particular as a punch bolt or punch nut.
 17. The punch rivetaccording to claim 1, wherein the rivet shank has an essentiallycylindrical shank outer face or a shank outer face provided with anaxial ribbing.
 18. A punch rivet with a rivet head and a rivet shankwith a central shank hole that have a common central axis X, wherein therivet head has an essentially cylindrical head outer face of a specifiedhead diameter d_(K), the rivet shank has an essentially cylindricalshank outer face of a specified shank outer diameter d_(N) and anessentially cylindrical shank inner face of a specified shank innerdiameter d_(i) delimiting the central shank hole, the head outer faceand the shank outer face are connected by means of a conical or slightlycurved underhead chamfer and an underhead radius R₄, which radius mergestangentially both into the underhead chamfer and into the shank outerface, and the shank outer face and the shank inner face are connected atthe rivet foot end via a radially outer first radius R₁ and a radiallyinner second radius R₂ that merge into one another tangentially, whereinthe common tangent Tan encloses an angle α with a radial plane of thepunch rivet, wherein the first radius R₁ merges tangentially into theshank outer face or is replaced by a chamfer of corresponding length,and the second radius R₂ is connected to the shank inner face via athird radius R₃, which radius merges tangentially both into the secondradius R₂ and into the shank inner face, and wherein the following valueranges hold true for the first radius R₁, the second radius R₂, thethird radius R₃, and the angle α:R ₁=0.3±0.2 mmR ₂=(0.7 to 1.2)(d _(N) −d _(i))/2R ₃=0.8±0.4 mmα=5°±10°.